Machine for producing gears



Dec. 7, 1937. n.. o, cARLsEN MACHINE FOR PROADUCING GEARS Filed Sept. 9,1935 4 Shees-Sheetl 1 l'mventor ew Jttneg Dec. 7, 1937. L. o. cARLsENMACHINE FOR PRODUCING GEARS Filed sept. 9, 1955 4 sheets-Sheet 2 npentor(ttorneg Dec. 7, 1937. L. o. cAQLsEN MACHINE FOR PRODUCING GEARSsheets-sheet 5- Filed Sept. 9, 1935 Dec. 7, 1937. A L. CARLSEN 2,101,237

MACHINE FOR vPRODUCING GEARS' Filed sept. 9, 1935 4 Sheng-sheet 4:inventor Gttorneg Patented Dec. 7, 1937 UNITED f. STATES OFFICE iMACHINE Foa PnonUolNc casas Leonard 0. Carlsen, Rochester, N. Y.,assignor to Gleason Works, Rochester, N. Y., a corporation of New YorkApplication September 9, 1935, Serial No. 39,675

1e claims.y

Y nism of the reciprocating type for machines for Where a frictionoperating means is employed, is

open to the further, Very serious objection that the movement'r of thetool to and from cutting position is not adjustable with reference tothe stroke of the tool slide. The same amount of movement of the toolslide in either direction must take place, after reversal of the slide,in order to swing the tool into cutting position or Withdraw ittherefrom. The result is that for a given job, the tool may not be movedinto cutting position until the tool slide is traveling at high speedwith the consequence that the tool Will strike the work withconsiderable force, setting up a chatter and causing a poor toothsurface finish. The force of impact of the rapidly traveling tool uponthe relatively stationary blank also causes comparatively rapid dullingof the tool.

A principal object of the present invention is to provide an improvedreciprocating tool mechanism in which the movements of the cutting toolto and from cutting position at the ends of its stroke may be effectedpositively and at any desired point in the stroke.

A further object of the invention is to provide a reciprocating toolmechanism which will be substantially silent in operation.

Another object ofthe invention is to provide an improved reciprocatingtool mechanism in which the tool will be held positively in cuttingposition during the cutting stroke so as effectually to obviate anychatter during cutting.

A further object of the invention is to provide a reciprocating toolmechanism in which the movement of the tool to and from cutting positionis effected by a bodily displacement oi the tool at right angles to thedirection of the cutting stroke so that the tool can be moved quicklyclear (Cl. S30- 9) of the work at the end of the cutting stroke andquickly returned into cutting position at the end Yof the idle, returnstroke.

Another object of the invention is to provide improved means forsupporting the reciprocating tool mechanism in a bevel gear cuttingmachine, soY as to provide a firm and rigid support for the same in anyposition of angular adjustment ofV the tool slide.

Inthe preferred embodiment of the present invention, the tool is secureddirectly to the tool slide, which is reciprocated to produce the cuttingstroke, and the slide is mounted upon a ram which is movedintermittently by a cam in a direction at right angles to the directionof stroke of the slide to move the tool to and from cutting position.The ram is mounted in an adjustable rocker member which issemi-cylindrical in shape and which can be adjusted angularly to adjustthe direction of the path of the tool in its cutting stroke.

The invention is shown as applied to a machine of the type disclosed inthe U. S. patent to Bauer and Carpenter, No. 2,000,209, of May '7, 1935.Through the use of the improved reciprocating tool mechanism of thepresent invention', it has been possible to make certain improvements inthe nishing tool end of the Bauer et al. machine and these improvementsalso constitute part of the present invention.

In the machine of the Bauer et al. patent, the Valternate feed andwithdrawal movementsof the tools for depth of cut and indexing purposes,respectively, are produced by reciprocation of a slide upon which theWhole tool mechanism is mounted and this slide is mounted upon asemi-cylindrical cradle which is oscillated to produce the generatingmotion of the tools. In the improved construction of the presentinvention, the feed and withdrawal motions of the tools are produced by'bodily movement of the rams which, as above described, also produce themovements of the tools to and from cutting position at the ends of thetool strokes. i rther, the rams are mounted in angularly adjustablerocker members that, in turn, are mounted in a full circular cradlewhich vis oscillated to produce the generating motiorn A furtheradvantage of the present invention is the reduction in weight or" theparts which move during cutting. Where the clapper blocks are mounted onthe slides, the Weight of the slides is very materially increased andthere is much greater liability of vibration than in the mechanism ofthe present invention.

A still further advantage of the present invention is the reduction inlength of stroke of the tool slides which it makes possible. Thiseffects a great saving in the time of cutting a gear. The tools can bemoved to and from cutting position at the ends of the stroke of slidewhile the crank, which reciprocates the slides, is rotating through thatangle of its movement which is least eiective in producing lengthwisemovement of the slides. Over-travel of the slides beyond the ends of thegear teeth is therefore held to a minimum.

The principal objects of the invention have been described above. Otherobjects of the invention will be apparent hereinafter from thespecification and from'the recital of the appended claims.

In the drawings:

Fig. l is a fragmentary View, showing in side elevation a reciprocatingtool mechanism constructed according to the preferred embodiment of thepresent invention;

Fig. 2 is a view looking at the rear of the column of a gear cuttingmachine upon which the tool mechanism is mounted, and showing parts ofthe drive to the tool mechanism and to the cradle;

Fig. 3 is a sectional View through the tool `mechanism, takensubstantially on the line 3-3 of Fig. 1;

Fig. e is a developed sectional View through the tool mechanism on aslightly smaller scale than Fig. 3 and taken substantially on the line d-l of Fig. 1;

Fig. 5 is a fragmentary end elevation, looking at the rear of the toolrams and showing also .the supporting rocker members therefor;

Fig. 5 is a plan view on a greatly reduced scale of one of the rockermembers and associated parts;

Fig. 7 is a fragmentary sectional View on the line 'l-l of Fig. 4,showing part of the mechanism for oscillating the tool slides;

Fig. 8 is a fragmentary View showing in detail the means for adjustingthe depth of tool feed;

Yand

Fig. 9 is a detail of the driving connection between the actuating plateand the tool slides. The invention for convenience will be described inconnection with one possible application to a `machine of the type ofthe Bauer et al. patent.

'upon the column l and partly upon the cap `member le which is securedto the column III by bolts i'i (Fig. 2). The cradle is held againstaxial movement on the column by a flange or shoulder 23 formed. on thecolumn and by the semi-circular retaining plates 24 (Figs. l and 4)which are bolted to the column and to the cap member I6.

Mounted in the cradle il for angular adjustment therein are a pair ofrocker members I8 and i8 (Figs. 3 and 5). Each of these rocker membersis formed with arcuate guide or bearing surfaces I9 and 26 that areadapted to engage and. seat on cylindrical ways 2i and 22, respectively,formed internally in the cradle. One of the rocker members i3 carriesthe upper tool of the tool mechanism, the upper tool slide and the partsfor imparting the relieving motion to this tool. The other rocker memberi8 carries the lower tool, the lower tool slide and the parts forimparting the relieving motion to this tool. The two rocker members andthe parts carried thereby are identical in construction save for thereversal of parts required due to the different positions of the twotools. In the following description, only one of the rocker members willbe described in detail and corresponding parts of the other rocker unitwill be denoted by corresponding reference numerals primed.

Mounted upon the rocker members li) and i8', respectively, forreciprocation in a direction parallel to the axis of the cradle are rams25 and 25', respectively. Secured to the front ends of the rams 25 and25,'respectively, by screws 253 and 26', respectively are dove-tailedguides 2l and 27', respectively. These guides extend at right angles totheir respective rams.'

The upper tool slide 28 is mounted to slide upon the dove-tailed guide21 and the lower tool slide 28 upon the dove-tailed guide 2. Gibs 29'and29', respectively, are provided to take up wear of the slides or guideswith use.

Mounted upon the tool slide 28 for longitudinal adjustment thereon is across-shaped plate 30 (Figs. 3 and l) and mounted upon the tool slide 28for longitudinal adjustment thereon is a corresponding plate 3e. Theplates 3Q and v363 are provided with tongues 35 and 35', re-

spectively, which engage in elongated slots 35 and 36', respectivelyformed in the slides 28 and 28', respectively and which guide the platesin their adjustment on the slides.

Adjustably mounted upon the plate 30 is a tool holder 36 and adjustablymounted upon the plate 3D is a tool holder 36. The vertical portions ofthe plates 30 and 30', respectively, t into slots formed in the backs ofthese tool holders, as clearly shown in Fig. 3, and form guides uponwhich the tool holders are adjustable. The upper tool holder 36 isadjusted upon 'the plate 30 by a screw 31, while the screw 371' servesto adjust the lower tool holder 36 upon the plate 30.

The tool holder 36 is adjusted longitudinally upon the upper tool slide28 by a screw 3l which threads into the upper tool slide and abutsagainst one end of the tool holder 36 while the lower tool holder 36' isadjusted upon the lower tool slide 28 by a screw 3l which threads intothe lower tool slide and abuts against one end of the tool holder 36.Locknuts 32 and 32", respectively, are provided for the two adjustingscrews. The tool holders 36 and 36', respectively, are secured to theupper and lower tool slides, respectively, in any position of theirdescribed longitudinal and lateral adjustments thereon by bolts 33 and33, respectively, which pass through elongated slots 34 and 34',respectively in the tool holders 36 and 36', and thread into the upperand lower tool slides 28 and 28',

respectively. The lateral adjustment required at i vthe two tools forpressure angle.

coupling,

v cradle I `any time for the tool holders is very slight and the slots34 and 34' are enough wider than the V'secured to the lower tool holder36' by screws 38'.

Wedge shaped washers 39 and 39', respectively, are provided inconjunction with the two tool holders to prevent slippage of the twotools and wedge members 40 and 4D', respectively, are provided inconjunction with the two tools to adjust The use of these wedge membersis old in the art and need not be further described here.y The two toolsT 5 and T shown are planing toolsV of standard construction such as areordinarily employed in cutting straight tooth bevel gears.

The toolslides 28 and 28' are reciprocated on the guides 21 and 21'l tomove the tools lengthwise of the tooth surfaces of the gear being cutandthe tools cut on the strokes of the slides in one direction and arewithdrawn clear of the blank on their return strles. The movement of thetools to and from cutting position at the ends of the strokes of thetool slides, is effected by movement of the rams 25 and. 25'. Themechanism for reciprocating the tool slides will be described first.V

Mounted upon the column l0 is a drive motor |40 QFig.' 2) which drivesthrough a suitable the bevel pinion |42. This pinion meshes with a bevelgear |43 which is secured to a shaft |44. The shaft |44 has a spur gear|48 secured to it which meshes with a spur gear 48. The latter gear hasa splined connection with a crank shaft 41 (Fig. 4). The crank shaft 41is rotatably and slidably mounted in bearings 48, 49 and 50, the bearing48 is secured in the cover plate 52 of the gear housing 53 that issecured by bolts 54 to the column I8 and cap member I6.

The bearings 48 and 50 are integral with the A bushing 56 is mounted inthe bearing 58 for direct support of the front end of the crank shaft.The parts |40, |42, |43, |44 .and |49 correspond to the identicallynumbered parts shown in the Bauer et al. patent and may be identicalwith-these parts.

The shaft 41 is of reduced diameter as denoted at 51 to form the crank.A connectingrarm 58 (Figs. 4 and 7) is connected to this portion 51 ofthe shaft by a cap member 59 and bolts 60. The connecting arm 58 issecured to a shaft 62 that is suitably mounted in the cradle. An arm 83is Y secured to the shaft 62 by bolts 64 and this arm is keyed to ashaft 85. The shaft is journaled in the bearings 86 and 81 which aresuitably secured to the cradle |I. The arm 63 isv held against axialmovement on the shaft 85 by a nut 58 which threads d'nto `the shaft andholds the arm 83 against a shoulder formed on the shaft.

The shaft 65 is formed at its front end with an enlarged head or plate1U (Figs. 4, 9 and 1). A diametrical slot or groove 1| is formed in thefront face of this plate and a pair of blocks 12 and 12' are adjustablymounted in thisgroove for adjustment radially of the axis of the shaft55. The blocks 12 and 12' are secured in any adjusted position on theactuating plate 10 by nuts 58 and 69', respectively. These nuts threadon the pins 14 and 14', respectively, which are integral with the blocks12 and 12', respectively,

and extend rearwardly therefrom through the slots 19 and 19',respectively in the actuating plate.

Pins 13 and 13, which are integral with the blocks 12 and 12',respectively, extend forwardly from these Yblocks and form pivots forblocks 83 and 83', respectively, which engage, respectively, in slotsformed in the slides 28 and 28'. Side- 95 walls of these slots in theslides are indicated at 84 and 84', respectively in Fig. 1.

From the preceding description it will be seen j that as the crank shaft41 rotates,.an oscillating movement is imparted to the shaft 65 andplate il() 18 and that the oscillating plate 1|)` through'the block .andpin` connections described imparts reciprocating movements to the upperand lower tool slides. Since these slides are connected to the plate 10on opposite sides of the shaft 65915 the tool slides move simultaneouslyin opposite directions.

The rams 25 and 25' are reciprocated to mov the tool slides to and fromcutting positlon'and they, too, move in opposite directions so that as@.20 the tool slides reciprocate one tool is in cutting position andmoving in one direction and the other tool is in relieved (non-cutting).position and moving in the opposite direction. The movements of therams are controlled from a cam 15 25 (Fig. 3) which is keyed to thecrankshaft '41 and which is` secured against axial movement relative tothat shaft bya nut 16 which threads onto the shaft and holds the camagainst a shoulder formed on the shaft. The cam is a face 30 cam andengages with a pair of rollers 11 and 11 that are secured respectively,to studs 18 and 18'. These studs are journaled on sets 80 andrespectively, of anti-friction bearings in sleeves 8| and 8|',respectively, that are threaded, 35 respectively, in the rams 25 and25'.l The studs are locked against axial movement relative to the setsof bearings 88 and 80 by nuts 82 and 82', respectively. Y I

The operative front `face of the cam 15 isf-,4.50 formed with two dwellsand with a rise and a return connecting these two dwell portions. Therise is to move the tool slides to cutting position, the following dwellis to hold the tools in cuting position during the cutting strokes ofthe 1.45 tool slides, the return is to move the tool slides from cuttingposition at the ends of their cutting strokes and the second dwell is tohold the tool slides out of cutting position during their returnstrokes. Since the two rollers 11 and 11' engage the cam 15 atdiametrically opposed points one tool will be out of cutting positionwhile the other tool is in cutting position and one tool will be movedinto cutting position while the other is being withdrawn therefrom. Thecam 15 5,55 being mounted on the crank shaft 41 is directly timed to therotation of the crank shaft. In each revolution of the crank shaft, eachtool slide makes a forward stroke and a return stroke and during itsforward stroke, the tool slide is in 30 cutting position while duringitsreturn stroke, the tool slide is in relieved (non-cutting) position.

To make the movements of the rams as smooth as possible and to minimizethe frictlonal resist-L615 ance to their movements and reduce the powerconsumption, it has been found desirable .to mount the rams uponanti-friction bearings, as shown. The rams are of Yconsiderablelateralldi- 70 mention and are of the cross sectional shape shown mostclearly in Fig. 5. At its front end, the ram 25 is mounted in sets ofspaced roller bearings and at its rear end in sets of spaced rollerbearings 86 and 81. 'Ihe ram 25'k is mount- 575 ed in corresponding setsof roller bearings 85', -86 and 81.

'Ihe rollers 11 and 11 are held against the operative surface of the cam15 and the rams 25 and 25 are moved clear of the blank at the end of thecutting strokes by separate spring-pressed plungers, one of which isdenoted at 95 in Fig. 6. AEach plunger is housed in a rocker member andextends parallel to a ram. The bore of the rocker vmember I8. in whichthe plunger 95 is housed is designated at 95 and the coil spring whichactuates this plunger is designated at 91. The plunger engages at itsrear end with a plate 98 (Figs. 5 and 6) which is secured by screws 99to the rear end of the ram 25.

The tools make a plurality of cutting strokes during the cutting of atooth of the gear blank, being fed into the blank to cut the tooth tothe desired depth. After the desired depth of tooth has been cut, thetools are withdrawn fully clear of the blank and the blank is indexed.

The feed of the tools into depth and their periodic withdrawal forindexing is effected by a cam |08 that is rotatably mounted upon the camshaft 81 (Figs. 3 and 4). This cam |00 is mounted upon anti-frictionbearings liti and |82 which are mounted upon the shaft. The cam is heldagainst axial movement relative to the shaft by the nut |03 whichthreads onto the shaft 51 and engages the inner races of the bearing lIl I.

A roller |85 (Fig. 2) which is secured to a stud .|06, engages in thetrack way |81 of the cam |59. This stud is secured to the housing 53 ina manner now to be described so that as the cam |88 rotates, axialmovement will be imparted to the -cam and to the shaft 41 and the partsaxed thereto.

The stud |08 is secured by screws |08 to a plate I I0. This plate I I isadjustabl-y secured by bolts to the housing 53. The bolts pass througharcuate slots 3 in the plate l0 and thread into the housing.

There is a pin I4 integral with the stud |86 and projecting from theouter end thereof. This pin is eccentric of the roller |05, as clearlyshown in Fig. 8. The result is that when the plate lli) is adjustedangularly, Athe feed cam |56 will be moved axially and with it the rams25 and 25 to determine the depth of feed of the tools T and T into thework. The angular adjustment of the plate ||0 is effected by rotation ofthe screw I|5 which threads into a lug I 6 that is integral with theplate I I8. 'Ihe screw I I5 abuts at its opposite ends against the wallsof the pocket in the housing 53 in which the plate I I9 is mounted.

The track of the cam |00 is so designed as to produce successively the.required feed movement to the tools into full depth position, thewithdrawal of the tools fully clear of the blank after the tooth hasbeen cut to full depth, and a dwell While the tools are withdrawn whichis of sufficient duration to permit the indexing of the blank to becompleted before the feed begins anew.

Positive stops are provided to limit the forward Imovements of the ramand determine precisely the positions of the tools on their cuttingstrokes. The positive stops comprise blocks 90 and 80', respectively,which are secured by screws 9| and 9|', respectively, to the rams 25 and25', respectively. These blocks are adapted to engage with studs 92 and92', respectively, which are threaded into the rocker members I8 andI8', respectively.

YTo maintain alignment between the actuat- Ving plate y1|] and the toolslides 28 and 28' is adapted to engage in a circular groove |22 that isformed in the cam member |00. As the cam vmember |88 is moved axially onthe shaft 41 due to the engagement of the roller with the track of thecam member, the yoke member |20 will also be moved axially and impartthe desired movement to the actuating plate to maintain this plate atall times in correct alignment with the tool slides.

The cam |08 is driven from a shaft |81 (Fig.

2) through the bevel gearings |88, |89, the shaft |25, the worm |26, theworm wheel |21 (Figs. 2 and 4) the spur gear |28 and the spur gear |29.The spur gear |29 is integral with the cam |00. The spur gear I 28 iskeyed to the hub of the worm wheel |21 and is secured to the worm wheelby screws |30. The worm wheel |21 is journaled on a stub shaft |32 thatis secured at opposite ends in the housing 53 and in the cover 52therefor. The shaft |25 which is made in two parts connected together bythe couplings |33'\ is journaled at opposite ends on anti-frictionbearings |32 and |35, respectively, in the column I8 and housing 53,respectively.

The oscillating generating motion of the cradle I is produced byrotation of a cam 2|8. This cam is driven from the'shaft |81 (Fig. 2)through bevel gearing including the gear 2|0, the shaft |2, the Worm 2|3and the worm wheel 2M. The

cam 2|6 and worm Wheel 2I4 are keyed to a common shaft 2| 5. A roller2|1 engages in thev track of the cam 2|6. This roller is mounted in alever arm 2|8 which is pivoted at 2|9 in the column of the machine. Thelever 2 I8 is slotted at its other end to receive the T-bolt 220 whichconnects the lever pivotally with the lower end of a turn-buckle 222.The upper end of this turn-buckle is pivotally connected by means of thepin 223 with the arm |35 that extends from one side of the cradle Theparts |81, |88, |89, 2|0, 2|2, 2|3, 2I4,

2|5, 2|8, 2|9, 220, 222 and 223 may be the Same parts as are denoted bythe same reference numerals in the machine of the Bauer et a1. patent.

The adjustment of the tools for tooth angle to conform to the angle oflengthwise convergence of the opposite sides of the teeth of a taperedgear to be cut is effected by angular adjustment of the rocker membersI8 and I8. There are segments |58 and |50 (Figs. 1 and 6) secured to therocker members I8 and |8, respectively. Journaled in the gibs |5| and|5I' which hold the rocker members against axial movement in the cradleII are stub shafts |52 and |52 to which are secured pinions |53 and |53'which mesh with the segments |50 and |50' respectively. By rotating thestub shafts |52 and |52', the rocker members can be adjusted `accuratelyto cause the tools to travel in paths converging at any desired angle.The gibs 5| and I5I are graduated to read against zero marks on the faceof the cradle to permit this adjustment to be made accurately. The gibs|5I and |5I are semi-circular and are secured to the cradle by screws|55 (Fig. 4).

The operation of the improved tool mechanism have been cut lby Will beapparent from the preceding description, but may be briey summed uphere.

f As the shaft 41'rotates, an oscillating motion is imparted to theshaft 65 through the linkage 58-63 (Figs. 4 and 7). 'I'his produces anoscillating motion of the actuating plate 10 which through the blocks 12and 12, the pins 13 and 13 and blocks 83 and 83 imparts yreciprocatingmovement to the tool slides 28 and 28', causing the tools T and T tomove longitudinally back and forth across the face of the gear beingcut. `The connections of the tool slides with the actuating plate aresuch that when one tool is cutting,-the other tool is clear of the cutand is being returned. The cam 15 (Fig. 4) which is securedto the shaft41 and which rotates therewith operates the rams'25 and 25 upon whichthe tool slides are mounted to move the tools to and from cuttingposition, maintain. them in cutting position during the cutting strokesand maintain them out of cutting position durin the return strokes ofthe slides. l

vDuring the Whole of the time that the tools are reciprocating back andforth, Athey arealso fed into the gear blank to cut teeth of the desireddepth. 'Ihis feedqmovement is produced by a depthwise movement of therams 25 and 25 through the action of the feed cam |00. This cam engagesthe stationary roller |05 and is sev' cured to the shaft 41 so as toimpart an axial movement to the shaft 41 as the cam rotates. Theactuating plate 10 is maintained in alignment`r with the tool slidesduring the feed movement and subsequent withdrawal by action of fthe'yoke-member |20 which engages in the slot |22 of the cam |00 andwhich causes the shaft 65 to be moved axially as the cam |00 is movedaxially.

' When opposite sides ofaa tooth of the gear the reciprocating tools,the tools-are Withdrawnclear of the blank by action ofthe cam and thespring-pressed plungers 95 which hold the rollers 11 and 11 against thecam 15.r Y'When the tools have been withdrawn, the blank may be indexed.

,While the invention has been described in con-V nection With a machineof the type of the Bauer et'al. patent, it will berobvious that it isdirectly applicable to'any type of machine employing reciprocating toolsfor cutting straight bevel gears and'moreover, that the features thereofare applicable to any machine employing a planing tool for cutting gearseither with straight or longitudinally curvedrteeth and either taperedor.cylindrical. The present application is intended to cover anyvariations, uses, or adaptations of the invention following, in general,the principles of the invention and including such departures from thepresent disclosure as come within known or customary practice in thegear art and as may be applied to the essential features hereinbeforeset forth and as fall Within thescope of the invention or the limits ofthe appended claims.

I-Iaving thus described my invention, what I claim is:

1. In a machine for producing tapered gears, a 'frame having internalcircular Ways, a cradle mounted on said ways' and oscillatable on saidframe and having anl internal bore and circular ways formed internallytherein Which arespaced from one another longitudinally of the bore, apair of supporting members mounted in the bore of said cradle and eachhaving spaced arcuate bearing surfaces to seat on said Ways, a toolslide reciprocably mounted on each of'said supporting' members, a toolmounted on each slide, means for adjusting said supporting membersangularly on said cradle to adjust the paths of movement ofthe toolslides relative to one another, and means carried by the cradle forreciprocating the tool slides.

2. In a gear cutting machine, a support, a pair of rams reciprocablymounted on said support, a tool slide .reciprocably mounted on each ramfor movement in a directionat an angle to the direction of movement ofthe ram, means for simultaneously reciprocating said slides in oppositedirections, .a single cam for controlling the movements of said rams andadapted to move the tool slides to and from cutting position at oppositeends of the strokes of said slides, and means operatively connectingsaid rams to said cam at diametrically opposed points of the cam path sothat VWhen one slide is in cutting position, the other slide is removedtherefrom.

3. In a gear cutting machine, a support, a ram reciprocable in saidsupport, a slide reciprocable on said ram in a -direction at an angle tothe direction of reciprocation of said ram, a rotatable crank-shaft,means operatively connecting the crank-shaft to said slide toreciprocate the same to effect cutting and return strokes of said slide,a cam secured to said crank-shaft and operatively connected to said ramto reciprocate the same to move the tool slide to and from cuttingposition at opposite ends of its stroke, means for rotating said shaft,and means for moving said shaft bodily to effect depthwise feed movementof the tool.

4. In a gear cutting machine, 'a support, a ram reciprocable in saidsupport, a slide reciprocable on said ram in a direction at an angle tothe direction of reciprocation of said ram, a rotatable crank-shaft,means operatively connecting the crank-shaft to said slide toreciprocate the same, a cam secured to said crank-shaft and operativelyconnected to said ram to reciprocate the same, a second cam rotatablymounted on said crank-shaft but secured against axial movement relativethereto, a member cooperating with said second cam and xed to saidsupport, means for rotating said second cam to impart depthwise feed andWithdrawal movements to the tool, and means for rotating saidcrank-shaft to impart alternate cutting and return movements to saidtool slide and alternately move the same to and from cutting position.

5. In a gear cuttingv machine, a support, a pair of rams reciprocablymounted in said support, a slide reciprocably mounted on each of saidrams for movement in a direction at right angles to the direction ofmovement of the rams, a tool secured to each slide, a rotatablecrank-shaft, means operatively connecting said shaft to said slides toreciprocate said slides simultaneously in opposite directions onrotation of said shaft, a cam secured to said crank-shaft to rotatetherewith and adapted to control the movements of said rams, meansoperatively connecting said rams `to said cam to cause one slide to bemoved into cutting position While the other is removed therefrom, asecond cam rotatably mounted on said crankshaft but held against axialmovement relative thereto, a relatively fixed member cooperating withsaid second cam to impart axial movement to said crank-shaft on rotationof 'said second cam, and means for rotating said crank-shaft and saidsecond cam.

6. In a gear cutting machine, a pair of recipesv 'fof

therein, a tool mounted on each of said slides, a rotatable crank-shaft,an actuating member operatively connected to Said crank-shaft to beoscillated on rotation of said crank-shaft, and means operativelyconnecting said actuating member to said slides to reciprocate saidslides on actuation of said member comprising a pair of blocks mountedon said actuating member for adjustment thereon radially of the axis ofoscillation of said member and. adapted to be secured i-lxedly to saidmember after adjustment, a pair of blocks mounted in the slots of saidslides and slidable therein, and means pivotally connecting each of thelast named blocks to one of the iirst named blocks.

7. In a gear cutting machine, a pair of tool slides, a rotatable memberfor reciprocating the tool slides simultaneously in opposite directions,means for actuating said member, a reciprocable member upon which eachtool slide is mounted, means for reciprocating the last named memberssimultaneously in opposite directions to move the tool slidesalternately to and from cutting position, means for moving thereciprocable members bodily together and independently of theirreciprocating movements to impart alternate feed and withdrawalmovements between the tools and the Work, and means for moving therotatable member bodily With the reciprocable members to maintainalignment of said parts during the feed and withdrawal movements.

8. In a machine for producing gears, a pair of reciprocatory supports, aslide mountedY on each support for movement thereon in a direction atright angles to the direction of movement of its support, a tool securedon each slide, a rotary member for moving the slides simultaneously inopposite directions longitudinally of the tooth surfaces of the Work, arotary member for moving said supports simultaneously in oppositedirections to move the tools toward and from the Work, and means forrotating said members simultaneously in timed relation.

9. In a machine for producing gears, a pair of reciprocatory supports, aslide mounted on each support for movement thereon in a direction atright angles to the direction of movement of the support, a tool mountedon each slide, a crank and means operatively connecting the crank to theslides to simultaneously reciprocate the slides in opposite directions,a rotary cam and means operatively connecting the cam to the supports toreciprocate the same simultaneously in opposite directions to move thetools toward and from the Work, and means for rotating the crank and camin timed relation.

10. In a machine for producing gears, a pair of reciprocatory supports,a slide mounted on each support for movement thereon in a direction atright angles to the direction of movement of the support, a tool securedto each slide, means for moving the supports simultaneously in oppositedirections, and means for reciprocating the slides simultaneously inopposite directions in timed relation with the movement of saidsupports.

11. In a machine for producing' gears, a pair of reciprocatory supports,a slide mounted on each support for movement thereon in a direction atright angles to the direction of movement of the support, a tool securedto Veach slide, means for moving the supports simultaneously in oppositedirections, means for reciprocating said slides simultaneously inopposite directions in timed rcable tool slides, each having a slotYformed relation with the movement of said supports, and' means formoving said supports and the slidereciprocating means bodily togethertoward and from the Work.

12. In a machine for producing gears, a frame, a pair of ramsreciprocably mounted on the frame, a guide carried at one end of eachram, means connected to each ram for reciprocating the ramssimultaneously in opposite directions, a slide mounted to reciprocate oneach guide in a direction at right angles to the direction ofreciprocation of the corresponding ram, means for reciprocating theslides simultaneously in opposite directions in timed relation with thereciprocation of the rams, and means for moving the ram-reciprocatingmeans alternately forward and back in the direction of movement of theram to impart alternate movements of feed and Withdrawal to the tools.

13. In a machine for producing gears, a frame, a pair of ramsreciprocably mounted on the frame, a slide reciprocably mounted on eachof said rams for movement in a direction at right angles to thedirection of movement of the rams, a tool secured to each slide, arotatable crank shaft, an actuating plate, means operatively connectingthe crank shaft 'to the actuating plate to oscillate the same, meansoperatively connecting the actuating plate to the slides to reciprocatesaid slides simultaneously in opposite directions, a cam secured to thecrank shaft to rotate therewith, means connecting the cam to the rams toreciprocate said rams simultaneously in opposite directions toward andfrom the Work, means for reciprocating the crank shaft axially to effectfeed and withdrawal movements between the tools and the Work, and meansconnecting the crank shaft to the actuating member to move the actuatingmember bodily with the crank shaft toward and from the Work so as tomaintain alignment between the actuating member and the tool slidesduring the feed and Withdrawal movements.

14. In a gear cutting machine, a frame, a pair of rams reciprocablymounted on the frame for movement toward and from the Work, a tool slidereciprocably mounted on each ram for movement in a direction at an angleto the direction of movement of the ram, a tool secured to each slide,means for simultaneously reciprocating said slides in oppositedirections, a rotary cam, means operatively connecting the rams to saidcam at diametrically opposed points of the cam path so that the ramsmove in opposite directions on rotation of the cam, and means forrotating the cam in timed relation With the means for reciprocating thetool slides.

15. In a gear cutting machine, a frame, a pair of rams reciprocablymounted on the frame for movement toward and from the Work, a tool`slide reciprocably mounted on each ram for movement in a direction at anangle to the direction of movement of the ram, a tool secured to eachslide, a crank shaft, means operatively connecting the crank-shaft tothe tool slides to reciprocate the tool slides simultaneously inopposite directions, a cam secured to the crank shaft to rotatetherewith, means operatively connecting the rams to said cam atdiametrically opposed points of the cam path so that the rams move inopposite directions on rotation of the cam, and means ior rotating thecrank-shaft.

16. In a gear cutting machine, a frame, a pair of rams reciprocablymounted on the frame for movement toward and from the Work, a tool slidereciprocably mounted on each ram for movement in a direction at angle tothe direction of movement of the ram, a tool secured to each slide, acrankshaft, means operatively connecting the crank shaft to the toolslides to reciprocate the tool slides simultaneously in oppositedirections,

l a cam secured to the crank shaft to rotate there- Withjmeansoperatively connecting the rams to said cam at diametrically opposedpoints 'of the cam path so that the rams move in opposite directions onrotation of the cam, means for rotating the crank-shaft, and means formoving the crank-shaft axially alternately toward and from the Work toeffect alternately feed and Withdrawal movements of the tools.

LEONARD O. CARLSEN.

